JP4750737B2 - Buffer valve structure - Google Patents

Description

  The present invention relates to an improved valve structure of a shock absorber.

  Conventionally, the valve structure of this type of shock absorber is, for example, embodied as a piston portion of a shock absorber for a vehicle or the like, and is called an annular window that communicates with each port at an outlet end of a port provided in the piston portion. An annular recess is formed, and an annular leaf valve is attached to and detached from a valve seat formed on the outer peripheral side of the annular recess to open and close the port.

  In particular, in a valve structure in which the leaf valve is separated from the valve seat by fixing and supporting the inner periphery of the leaf valve and bending the outer periphery, the damping force in the medium to high speed region increases and the riding comfort in the vehicle increases. In order to eliminate this, as shown in FIG. 4, the inner periphery of the leaf valve L is not fixedly supported, and the inner periphery of the leaf valve L is fixed to the piston rod R or the piston rod R as shown in FIG. A valve structure has been proposed in which the back surface of the leaf valve L is urged by a spring S in sliding contact with the outer periphery of a guide tube disposed on the outer periphery (see, for example, Patent Document 1).

In this valve structure, as shown in the figure, when the piston speed when the piston P moves downward is in the low speed region, the outer peripheral side of the leaf valve L bends with the urging position of the spring S as a fulcrum. Exerts substantially the same damping characteristics as the valve structure in which the valve is fixedly supported, and when the piston speed reaches the middle-high speed range, the pressure of the hydraulic oil passing through the port Po acts on the leaf valve L, and the spring S is attached. Since the entire leaf valve L lifts and retracts from the piston P in the axial direction against the force, the flow passage area becomes larger than the valve structure in which the inner periphery is fixedly supported, and the damping force is excessive. The ride comfort in the vehicle can be improved.
JP-A-9-291196 (FIG. 1)

  However, in the proposed valve structure as described above, although it is a useful technique in terms of improving riding comfort in a vehicle, it may be pointed out that there are the following problems.

  As described above, when the piston speed when the piston P moves downward in the drawing reaches the middle-high speed region, the leaf valve L moves backward from the piston P in the axial direction, and the moving direction of the piston P is reversed from there. Then, when it starts to move upward in the figure, the force that has pushed up the leaf valve L by the hydraulic oil until then decreases or disappears, so that the leaf valve L returns to the position where it abuts against the piston P. As described above, the leaf valve L repeats the reciprocating operation. During this reciprocating operation, the inner periphery of the leaf valve L is caught by the piston rod R or the outer peripheral surface of the guide cylinder, and the reciprocating operation is smoothly performed. The damping force generated by the shock absorber may not be stable because the reciprocating operation becomes unstable. In particular, when the leaf valve L is configured by laminating a plurality of leaves, the above-described pulling is not possible. Since the resistance due to the hook increases, the operation becomes increasingly unstable, there is no guarantee that each leaf will be properly laminated and return to its original position, and the seating state of the leaf valve L on the valve seat is also constant There is also a risk of not.

  Accordingly, the present invention has been made to improve the above-mentioned problems, and an object of the present invention is to provide a valve structure of a shock absorber that can stabilize the reciprocating operation of the leaf valve. .

To solve the above object, a first means for solving problems of the present invention comprises a valve disc which port is formed, a shaft member rising from the axial center of the valve disc, is the shaft member on the inner peripheral side with Once inserted and an annular leaf valve for opening and closing the ports are stacked on the valve disc, and biasing means for biasing the leaf valve in a direction for closing the port, the inner and the axis of the leaf valve in the valve structure of the damper provided with a movable intermediate member is interposed together with the leaf valve in the axial direction with respect to the shaft member between the outer periphery of the member, the interposed member, the leaf valve a cylindrical portion that is interposed between the outer periphery of the inner periphery and the shaft member, a flange which extends from one end periphery of the cylindrical portion receiving the biasing force of the biasing means to support the rear surface of the leaf valve Department and Provided, the axial length of the tubular portion is set to be longer than the axial length of the leaf valve, a recess to allow the entry of the tubular portion provided on the valve disc, the leaf valve laminated side end portion of the valve disc An annular window connected to the outlet end of the port; an annular valve seat on which the leaf valve is seated on an outer periphery of the annular window; and the leaf valve is configured by laminating a plurality of annular leaves, The outer diameter of the leaf and the minimum diameter leaf is set larger than the inner diameter of the annular valve seat.
The second problem-solving means of the present invention includes a valve disk in which a port is formed, a shaft member rising from the axial center of the valve disk, the shaft member being inserted on the inner peripheral side, and the valve An annular leaf valve stacked on the disk for opening and closing the port, a biasing means for biasing the leaf valve in a direction to close the port, and an inner periphery of the leaf valve and an outer periphery of the shaft member In the valve structure of the shock absorber provided with an interposed member that is interposed and movable in the axial direction with respect to the shaft member together with the leaf valve, the interposed member includes an inner periphery of the leaf valve and the shaft member. A cylinder portion interposed between the outer periphery and a flange portion that extends from the outer periphery of one end of the cylinder portion and supports the back surface of the leaf valve and receives the urging force of the urging means; Axial direction The length is set longer than the axial length of the leaf valve, a recess is provided in the valve disc to allow the cylindrical portion to enter, and the annular end connected to the outlet end of the port is provided at the leaf valve lamination side end of the valve disc. A window, an annular valve seat on which the leaf valve is seated on the outer periphery of the annular window, and three or more valve support portions that rise from the bottom of the annular window at equal intervals on the same circumference and support the front of the leaf valve The leaf valve is configured by laminating a plurality of annular leaves, and the outer diameter of the flange portion and the minimum diameter leaf is set larger than the inscribed circle diameter of the valve support portion. It is characterized by that.

  According to the valve structure of the present invention, since the interposition member is interposed between the leaf valve and the shaft member, the leaf valve can reciprocate stably and smoothly, and the shock absorber expands and contracts. The damping characteristics (the relationship of the generated damping force with respect to the expansion / contraction speed) are not different each time, and further, the occurrence of contamination can be prevented because the inner periphery of the leaf valve does not bite the outer periphery of the shaft member.

  Also, when the spring member receives the urging force of the spring at the collar part of the intervening member and the axial length of the cylindrical part is longer than the axial length of the leaf valve, the leaf valve moves backward and returns to the position where it contacts the valve disc In addition, the leaf valve can be reliably prevented from falling off from the interposition member.

  The valve structure of the present invention will be described below with reference to the drawings. FIG. 1 is a longitudinal sectional view of a base valve unit in which a valve structure of a shock absorber according to an embodiment is embodied. FIG. 2 is a plan view of a shock absorber valve disk in which a shock absorber valve structure according to an embodiment is embodied. FIG. 3 is a partially enlarged longitudinal sectional view of a base valve portion in which a valve structure of a shock absorber according to a modification of the embodiment is embodied.

  The valve structure of the shock absorber in one embodiment is embodied as a damping valve on the pressure side of the base valve 1 of the shock absorber D, as shown in FIG. A shaft member 4 rising from the axial center of the disk 2, an annular leaf valve 5 which is stacked on the valve disk 2 and opens and closes the port 3 when the shaft member 4 is inserted on the inner peripheral side, and the port 3 is closed. A spring 6 as an urging means for urging the leaf valve 5 in the direction to be moved, and an axial direction with respect to the shaft member 4 together with the leaf valve 5 interposed between the inner periphery of the leaf valve 5 and the outer periphery of the shaft member 4 And an intervening member 7 that is movable.

  On the other hand, a shock absorber in which the valve structure is embodied is well known and will not be described in detail, but specifically, for example, a cylinder 40 and a head member (not shown) that seals the upper end of the cylinder 40. ), A piston rod (not shown) that slidably penetrates the head member (not shown), a piston (not shown) provided at the end of the piston rod, and a piston within the cylinder 40. A rod-side chamber (not shown), a piston-side chamber 41 below the piston, an outer cylinder 42 provided outside the cylinder 40, a sealing member 43 that seals the lower end of the outer cylinder 42, and the valve The base valve portion 1 in which the structure is embodied, and a reservoir 44 that is formed between the cylinder 40 and the outer cylinder 42 and compensates for a change in the volume in the cylinder corresponding to the volume of the piston rod protruding and retracting from the cylinder 40 are configured. The cylinder 40 in the fluid, hydraulic fluid is filled in particular, hydraulic oil and the gas is sealed in the reservoir 44.

  In the base valve 1, when the pressure in the piston side chamber 41 rises during the compression stroke of the shock absorber D and the hydraulic oil moves to the reservoir 44 via the port 3, the hydraulic oil moves. The leaf valve 5 provides resistance to cause a predetermined pressure loss and functions as a damping force generating element that causes the shock absorber D to generate a predetermined compression side damping force.

  Hereinafter, the valve structure will be described in detail. As shown in FIGS. 1 and 2, the valve disk 2 includes a disc-shaped main body 8 having an insertion hole 9 through which a shaft member 4 is inserted in an axial center portion, and a main body. 8, an annular recess 10 provided at the end of the leaf valve stacking side, a plurality of ports 3 formed at equal intervals on the same circumference of the main body 8, and an end of the main body 8 on the leaf valve stacking side An annular window 11 formed at the end of the port 3 and connected to the outlet end of the port 3, an annular valve seat 12 on which the leaf valve 5 is seated on the outer periphery of the annular window 11, rises from the bottom of the annular window 11 at equal intervals on the same circumference Three valve support portions 13 that support the front face of the leaf valve 5 and suction ports 14 that are formed at equal intervals on the same circumference on the outer peripheral side from the port 3 of the main body 8 are configured.

  An annular leaf valve 5 is stacked below the valve disk 2 in FIG. 1, and the port 3 is opened and closed by the leaf valve 5. On the other hand, above the valve disk 3, A check valve 15 that opens and closes the suction port 14 is biased by the spring 16 and the suction port 14 is opened and closed by the check valve 15.

  Further, the valve disk 2 is fixed to the lower end of the cylinder 40 via the shaft member 4 to partition the piston side chamber 41 and the reservoir 44 from each other. That is, the port 3 allows the hydraulic oil to flow from the piston side chamber 41 to the reservoir 44 when the shock absorber D is compressed, and the suction port 14 extends when the shock absorber D extends. The check valve 15 is opened to allow hydraulic fluid to flow from the reservoir 44 toward the piston side chamber 41.

  The suction port 14 is a port that sucks in the hydraulic oil corresponding to the volume of the piston rod that is deficient in the cylinder 40 when the shock absorber D is extended, so that the check valve 15 operates through the suction port 14. The spring 16 is lifted from the valve disk 2 against the biasing force of the spring 16 so as not to give resistance to the oil flow as much as possible. The spring 16 biases the check valve 15 toward the suction port 14 side. As a result, the suction port 14 can be closed by the check valve 15 and the lift of the check valve 15 is quickly eliminated after the suction port 14 is opened.

  Further, it is considered that the open ends of the ports 3 and 14 are not blocked by the leaf valves 5 and the check valves 15 stacked on the valve disk 2.

  Further, in the illustrated case, eight ports 3 are provided at equal intervals, and the outlet ends of all the ports 3 are connected to the annular window 11. Then, from the bottom of the annular window 11, that is, between the outlet ends of the ports 3 in the annular window 11, three valve support portions 13 rise at equal intervals on the same circumference, and the leaf valve 5 is the annular valve. In the state of being seated on the seat 12, the front surface serving as the pressure receiving surface of the leaf valve 5 is seated on and supported by the valve support portion 13.

  The leaf valve 5 laminated on the valve disk 2 is configured as a laminated leaf valve by laminating a plurality of annularly formed leaves 5a, and the leaf valve 5 is laminated on the valve disk 2 to form an annular shape. In a state where the valve seat 12 and the valve support 13 are in contact with each other, the port 3 is closed by closing the annular window 11 connected to the outlet end of the port 3.

  In addition, the outer diameter of the minimum diameter leaf 5 a constituting the leaf valve 5 stacked on the interposition member 7 side is set larger than the inscribed circle diameter of the valve support portion 13. That is, the minimum outer diameter X of the leaf 5a indicated by the broken line in FIG. 2 is larger than the diameter of the inscribed circle Y of the valve support portion 13 indicated by the alternate long and short dash line.

  Note that the number of the leaves 5a in the leaf valve 5 may be arbitrarily determined depending on the damping characteristic realized by the present valve structure. For example, the leaf valve 5 may be constituted by one sheet.

Next, the shaft member 4 includes a base 4a fitted to the lower end in FIG. 1 of the cylinder 40, a flange 4b provided at the lower end on the outer periphery side of the base 4a, and a shaft portion that rises from the upper end axial core portion of the base 4a. 4c, and the flange portion 4b is sandwiched between the cylinder 40 and the sealing member 43 and fixed to the cylinder 40. The shaft portion 4c is an urging means in order from the bottom in FIG. 1 is inserted into the inner circumference of the spring 6, the interposition member 7, the leaf valve 5, the valve disk 2, the check valve 15, the spring 16, the spacer 17 and the valve stopper 18, and the tip which is the upper end in FIG. The disk 2 protrudes upward in FIG.

  In this way, each member described above is assembled to the shaft portion 4c, and among these members, the valve disk 2, the spacer 17 and the valve stopper 18 are formed on the outer periphery of the shaft portion 4c, and the step portion 4d formed on the outer periphery of the shaft portion 4c. The shaft portion 4c is fixed to the shaft portion 4c by being sandwiched by a nut 19 that is screwed to a screw portion 4e formed at the tip that is the upper end in FIG.

  Therefore, the leaf valve 5 and the interposed member 7 are not fixed with respect to the shaft portion 4c, and can move in the axial direction which is the vertical direction in FIG.

  The interposition member 7 interposed between the inner periphery of the leaf valve 5 and the shaft portion 4c of the shaft member 4 is slidably mounted on the outer periphery of the shaft portion 4c. Is a cylindrical portion 7a interposed between the inner periphery of the leaf valve 5 and the outer periphery of the shaft portion 4c, and a flange portion 7b extending from the outer periphery of one end which is the lower end of the shaft portion 7a in FIG. The cylindrical portion 7a includes a cylindrical socket 7c suspended from the lower end in FIG. 1, and a bearing 7d that is held in the socket 7c and slidably contacts the outer periphery of the shaft portion 4c. A spring 6 as an urging means is interposed between the back surface and the base 4a of the shaft member 4, and the interposition member 7 is urged toward the valve disk 2 side. Further, the outer diameter of the flange portion 7 b is set to be larger than the inscribed circle diameter of the valve support portion 13.

  The inner diameter of the cylindrical portion 7a is larger than the outer diameter of the shaft portion 4c, and only the bearing 7d having excellent slidability is in sliding contact with the shaft portion 4c. The portion 4c can be smoothly moved up and down without resistance. However, the bearing 7d can be omitted if the slidability is not inferior even if the socket 7c in the interposing member 7 is brought into sliding contact with the shaft portion 4c.

  Further, the axial length of the cylindrical portion 7a is set to be longer than the axial length of the leaf valve 5, and the tip that is the upper end in FIG. 1 protrudes upward from the leaf valve 5, A tapered portion 7e is formed on the outer periphery of the distal end so as to taper toward the distal end, facilitating insertion of the tubular portion 7a into the inner periphery of the leaf valve 5, thereby simplifying the assembly process.

  When the cylindrical portion 7 a of the interposed member 7 configured as described above is inserted into the inner periphery of the leaf valve 5 and assembled to the shaft portion 4 c of the shaft member 4 together with the spring 6, the interposed member 7 is biased by the spring 6. Since the rear surface of the leaf valve 5 is supported by the flange portion 7b of the interposition member 7, the leaf valve 5 is pressed together with the interposition member 7 toward the valve disk 2, and the front surface of the leaf valve 5 is The port 3 is closed by sitting on the annular valve seat 12 and the valve support portion 13.

  In this state, the tip of the cylindrical portion 7a enters the recess 10 provided in the valve disc 2 and does not interfere with the valve disc 2, and does not hinder the leaf valve 5 from being seated on the annular valve seat 12 and the valve support portion 13. It is like that. That is, the axial length of the concave portion 10 is set to be longer than the tip length of the cylindrical portion 7a protruding from the leaf valve 5, so that the cylindrical portion 7a can be allowed to enter.

  As described above, the leaf valve 5 is urged by the spring 6 via the interposed member 7, but the interposed portion 7 does not interfere with the valve disk 2, so that the leaf valve 5 supports the annular valve seat 12 and the valve support. In the state of being seated on the portion 13, all of the urging force of the spring 6 is supported by the leaf valve 5.

  In this embodiment, the outer diameter of the flange portion 7b and the outer diameter of the smallest diameter leaf 5a constituting the leaf valve 5 stacked on the interposition member 7 side are larger than the inscribed circle diameter of the valve support portion 13. Since the large diameter is set, even if the leaf valve 5 is seated on the annular valve seat 12 and the valve support portion 13, the leaf valve 5 will not be bent.

  As described above, the leaf valve 5 is supported by the annular valve seat 12 and the valve support portion 13 so that the initial deflection does not occur. Therefore, the port 3 is strongly blocked by the initial deflection of the leaf valve 5. There is no. Therefore, a large damping force is not generated at the initial stage of expansion / contraction of the shock absorber D, and expansion / contraction is performed only by dimensional management of the outer diameter of the leaf 5a, the outer diameter of the flange portion 7b, and the inscribed circle diameter of the valve support portion 13. It is also possible to prevent the initial generated damping force from varying from product to product. Further, since the cylindrical portion 7a can enter the recess 10 without interfering with the valve disk 2, a gap is formed between the leaf valve 5 and the annular valve seat 12 due to a dimensional error, and the port 3 is blocked. There is no risk of becoming insufficient. As described above, the valve support portion 13 is provided so as not to cause the initial deflection of the leaf valve 5, and three or more are equally spaced so that the leaf valve 5 can be stably supported without being biased. It is good to provide.

  If the valve support 13 is not provided, as shown in FIG. 3, the outer diameter of the minimum diameter leaf 5a constituting the leaf valve 5 laminated on the flange 7a and the interposition member 7 side is set as an annular valve. If the diameter is set to be larger than the inner diameter of the seat 12, it is possible to prevent the initial deflection from occurring in a state where the leaf valve 5 is seated on the annular valve seat 12, as in the case where the valve support 13 is provided. 3 can be prevented from being strongly blocked, and a large damping force is prevented from being generated in the initial stage of expansion and contraction of the shock absorber D.

  Moreover, the step part 4f which determines the movement limit to the downward direction in FIG. 1 with respect to the axial part 4c of the interposed member 7 is formed in the lower outer periphery of the axial part 4c, and the interposed member 7 with respect to the axial part 4c When moving downward to the limit of movement in FIG. 1, the stepped portion 4f comes into contact with the lower end of the bearing 7d to restrict further downward movement of the interposition member 7.

  That is, the leaf valve 5 is always urged in the direction of closing the port 3 by the spring 6, and when the pressure in the piston side chamber 41 exceeds a predetermined value, the spring 6 resists the urging force of the spring 6. , The entire leaf valve 5 is retracted from the valve disk 2 in the axial direction, that is, lifted downward in FIG. 1, and the leaf valve 5 is finally connected to the shaft portion 4c described above. The interposition member 7 moves backward until it comes into contact with the stepped portion 4f.

  Further, in the above description, the biasing means is the spring 6 which is a coil spring in the drawing, but a predetermined biasing force may be applied to the leaf valve 5, so that this is, for example, a disc spring or a leaf spring. Or an elastic body such as rubber.

  A spring 16 that urges the check valve 15 from the back side is interposed between the check valve 15 and the valve stopper 18, and the valve stopper 18 lifts the check valve 15 upward in FIG. And also serves as a spring receiver for the spring 16.

  Next, the operation of the valve structure will be described. As described above, the piston moves downward in FIG. 1 with respect to the cylinder 40 to increase the pressure in the piston side chamber 41, and the hydraulic oil in the piston side chamber 41 is ported. 3 and try to move into the reservoir 44.

  When the compression speed of the shock absorber D is in the low speed region, the leaf valve 5 is urged by the spring 6 and pressed so as to close the port 3, so that the outer periphery of the leaf valve 5 bends and leaves the leaf valve 5 The hydraulic oil passes through a gap between the leaf valve 5 and the annular valve seat 12, which is formed when 5 is separated from the annular valve seat 12.

  On the other hand, when the compression speed of the shock absorber is high and the pressure in the piston side chamber 41 becomes equal to or higher than a predetermined value, the force for pushing the leaf valve 5 downward in FIG. 1 increases, and the force overcomes the urging force of the spring 6, The entire leaf valve 5 is retracted from the valve disk 2 in the axial direction, that is, moved downward in FIG.

  At this time, the leaf valve 5 retreats in the axial direction together with the interposition member 7 due to the presence of the flange portion 7b, but the interposition member 7 is interposed between the leaf valve 5 and the shaft portion 4c. Since the leaf valve 5 is in sliding contact with the outer periphery of the shaft portion 4c, the inner peripheral side of each leaf 5a in which the axial length of the leaf valve 5 is very short is not caught by the outer peripheral surface of the shaft portion 4c. Can be smoothly retracted from the valve disc 2.

  In addition, since the retreating amount of the leaf valve 5 is regulated by the step portion 4e provided on the shaft portion 4c, the maximum gap formed between the leaf valve 5 and the annular valve seat 12 can be adjusted and necessary. As described above, it is possible to prevent the maximum gap from becoming large and the damping force from becoming too small.

  When the contraction speed decreases from that state or the shock absorber D shifts to the expansion stroke, the pressure in the piston-side chamber 41 becomes smaller than a predetermined value, and this time, the force that pushes the leaf valve 5 downward. The biasing force of the spring 6 wins and the leaf valve 5 is pushed up to the valve disk 2 side. However, since the bearing 7d of the interposing member 7 is in sliding contact with the outer periphery of the shaft portion 4c, the leaf valve is still used. The inner peripheral side of each leaf 5a having a very short axial length of 5 is not caught by the outer peripheral surface of the shaft portion 4c, and the leaf valve 5 is smoothly moved to the valve disc 2 side to lift the leaf valve 5. Can be eliminated.

  That is, according to the above description, in the valve structure in this embodiment, the leaf valve 5 moves forward and backward relative to the piston 1 more smoothly than the conventional valve structure. There is no delay in the return to the position where it abuts.

  Therefore, in this valve structure, since the interposition member 7 is interposed between the leaf valve 5 and the shaft member 4, the leaf valve 5 performs a reciprocating operation in the vertical direction stably and smoothly. Each time the shock absorber D expands and contracts, the damping characteristics (the relationship of the generated damping force with respect to the expansion / contraction speed) do not differ, and the inner periphery of the leaf valve 5 may bite the outer periphery of the shaft member 4. Since there is no contamination, the occurrence of contamination can be prevented.

  Further, since the flange portion 7b of the interposing member 7 receives the urging force of the spring 6, and the axial length of the cylindrical portion 7a is longer than the axial length of the leaf valve 5, the leaf valve 5 is retracted downward in FIG. It is possible to reliably prevent the leaves 5a from falling off the interposition member 7 when returning to the position where the valve disk 2 comes into contact.

  Further, since the urging force of the spring 6 is received by the flange portion 7 b of the interposing member 7, there is an advantage that even if the spring 6 is eccentric with respect to the leaf valve 5, the fulcrum of deflection does not shift.

  In the above description, the valve structure of the present invention has been described by using an example embodied in the damping valve on the pressure side of the base valve 1 of the shock absorber. However, it is embodied only in the damping valve on the expansion side or on both sides of the pressure expansion. Further, it can be embodied in any damping valve for expanding the piston portion, and is applied to a valve of a shock absorber that functions as a damping force generating element that generates a damping force. Of course it is possible.

  When this valve structure is embodied in the piston part, for example, when the valve structure in FIG. 1 is inverted and the shaft member 4 is embodied as a piston rod in the compression side damping valve, the expansion and contraction of the shock absorber D is reversed. In the situation, there is no delay in the closing of the port 3, and the situation in which the hydraulic oil freely passes through the rod side chamber and the piston side chamber through the port 3 without resistance is prevented. Sufficient damping force can be generated. On the other hand, when the valve structure is embodied in the expansion side damping valve of the piston portion, a sufficient damping force can be generated in the shock absorber from the beginning of the compression stroke. That is, the responsiveness of the damping force generation of the shock absorber D can be improved.

 It should be noted that the scope of the present invention is not limited to the details shown or described.

It is a longitudinal cross-sectional view in the base valve part in which the valve | bulb structure of the shock absorber in one Embodiment was actualized. It is a top view of the buffer valve disc in which the valve structure of the buffer in one embodiment was embodied. It is a partially expanded longitudinal cross-sectional view of the base valve | bulb part in which the valve | bulb structure of the shock absorber in the modification of one Embodiment was embodied. It is a longitudinal cross-sectional view of the conventional valve structure.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Base valve 2 Valve body 3 Port 4 Shaft member 4a Base 4b Ridge part 4c Shaft part 4d, 4f Step part 4e Screw part 5 Leaf valve 5a Leaf 6 Spring as an urging means 7 Interposition member 7a Tube part 7b in the interposition member The flange 7c in the intervention member The socket 7d in the intervention member The bearing 7e in the intervention member 8 The taper portion 8 in the intervention member 8 The main body in the valve disc 9 The insertion hole 10 in the valve disc Recess 11 The annular window 12 The annular valve seat 13 The valve support portion 14 Suction port 15 Check valve 16 Spring 17 Spacer 18 Valve stopper 19 Nut 40 Cylinder 41 Piston side chamber 42 Outer cylinder 43 Sealing member 44 Reservoir

Claims (3)

A valve disc which ports are formed, an annular leaf valve for opening and closing shaft member rising from the axial center of the valve disc, is laminated with the above shaft member is inserted into the inner circumferential side to the valve disc the port If a biasing means for biasing the leaf valve in a direction for closing the port, with respect to the shaft member with interposed said leaf valve between an outer periphery of the inner periphery and the shaft member of the leaf valve in the valve structure of the damper provided with a movable intermediate member in the axial direction, said interposed member has a cylindrical portion that is interposed between the outer periphery of the inner periphery and the shaft member of the leaf valve, extends from one end periphery of the cylindrical portion and a flange portion for receiving the biasing force of the biasing means to support the back surface of the leaf valve, the axial direction of the leaf valve the axial length of the tubular portion Length Set longer, a recess to allow the entry of the tubular portion to the valve disc is provided, the leaf valve laminated side end portion of the valve disc, an annular window connected to the outlet end of the port, above the outer periphery of the annular window An annular valve seat on which the leaf valve is seated, and the leaf valve is formed by stacking a plurality of annular leaves, and the outer diameter of the flange and the smallest diameter leaf is larger than the inner diameter of the annular valve seat. The valve structure of the shock absorber is characterized by being set to a diameter . A valve disk in which a port is formed, a shaft member rising from the axial center of the valve disk, and an annular leaf valve that is stacked on the valve disk and opens and closes the port when the shaft member is inserted on the inner peripheral side And an urging means for urging the leaf valve in a direction to close the port, and an interposition between an inner periphery of the leaf valve and an outer periphery of the shaft member, together with the leaf valve and the shaft member In the valve structure of the shock absorber provided with an interposition member movable in the axial direction, the interposition member includes a cylindrical portion interposed between an inner periphery of the leaf valve and an outer periphery of the shaft member; A flange portion extending from the outer periphery of one end of the cylindrical portion to support the back surface of the leaf valve and receiving the urging force of the urging means, and the axial length of the cylindrical portion is set to the axial direction of the leaf valve. Length The valve disc is provided with a recess that allows the tube portion to enter, and the valve disc has a leaf valve stacking side end, an annular window connected to the outlet end of the port, and an outer periphery of the annular window. An annular valve seat on which the leaf valve is seated and three or more valve support portions that rise from the bottom of the annular window at equal intervals on the same circumference and support the front of the leaf valve are provided, and a plurality of the leaf valves are provided. of an annular leaf formed by laminating, the flange portion and the smallest diameter of the leaf outer diameter of loose衝器 it, characterized in that it is set to have a larger diameter than the bore diameter of the valve support portion Valve structure. The buffer structure for a shock absorber according to claim 1 or 2, wherein a tapered portion is formed to be tapered on an outer periphery of a tip of the cylindrical portion .

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